Integrated energy system

ABSTRACT

This invention is a multiple diverse energy source driven energy integration and multiple use-point system: which includes system air pressure compensated variable pressure and volume delivery of compressed air from multiple air compression stations which discharge and store compressed air into an included interconnecting collection storage and distribution conduit multiple module grid system; of largest needed and commercially available size pipe to keep the pressure drop to a minimum, and from which the compressed air is withdrawn at multiple points of need; when and as needed, through synchronized dual-precision-controls to turn, at optimum RPM speed regardless of varying work loads, air motor drives for operation of conventional electrical generating equipment with varying customer-use-demand output work loads. The conduit-pipe systems are arranged in interconnecting, but isolable, multiple module grids ranging in size from those needed, for example, for a small town or a large individual user of electricity to large metropolitan areas and which may ultimately be interconnected into a large regional, national, or continental system. Natural energy sources including wind, tide, wave, thermal and solar power, as well as conventional fuels, may be utilized to provide the energy required to drive compressors to supply the air into the system. An improved wind turbine is included for the recovery and use of wind-power for compressing air on a vast scale in multiple installations.

CROSS REFERENCE TO RELATED APPLICATIONS

This is a division, of application Ser. No. 728,064, filed Sept. 30,1976, now U.S. Pat. No. 4,118,637 which is a continuation-in-part ofSer. No. 579,131 now abandoned, the entire disclosure of which isincorporated herein by reference.

BACKGROUND OF THE INVENTION

1. Field of the Invention

This invention relates to systems for providing useful energy in theform of electrical power, and more particularly to an improved systemfor utilization of multiple diverse energy sources in compressing largevolumes of air, collecting, storing and distributing the air in aconduit system including interconnecting multiple module gridsconstructed of large conduit-pipe, utilizing the air as and wherenecessary to operate equipment for generating electricity near thepoints of use.

2. Description of the Prior Art

The use of compressed air as a means to drive or operate numerousdevices is well-known, and compressed air was widely used in the earlydevelopment of modern industry. However, the development of oil and gaspowered direct drive universal electrical energy generating anddistribution systems have resulted in a virtual abandonment of thedevelopment of compressed air as a major industrial motive power.Consequently, air compression, storage, and transmission systems in usetoday generally include conventional branch and trunk type collectionand transmission lines of relatively small flow size, with conventionalair storage tanks, or accumulators, near the compressors and/or near thepoints of use. The storage tanks are expressly for the purpose ofbridging over short periods of high use where compressor and normal linecarrying capacities are normally overtaxed, and are not intended orbuilt for storage of several days reserve usage of compressed air.Pressure losses in such conventional compressed air systems is a highlylimiting factor in transmitting air in large volumes over anysubstantial distance.

The compressor installations in use today are generally single stagecompressors for delivering relatively high volumes of air at lowpressures, while two stages are used for medium pressures, and threestages for higher pressure, low volume air. This does not givesufficient volume-pressure automatic demand delivery flexibility inmeeting maximum use demands for compressed air with minimum compressorequipment for large scale use.

Conventional compressed air controls for air motors which turn multipleelectrical generators of power plants cannot adequately control thedelivery of the driving air with the precision control required to reachand maintain the different optimum speeds required for differentgenerators with varying work loads, due to the fact that such knownautomatic control devices generally regulate only air flow and not acombination of flow and pressure.

Electrical generating systems in use today normally make no provisionsfor storing energy during periods of low use for later utilizationduring times of peak use. This, generally, has resulted in discouragingthe utilization of natural energy sources for the generation ofelectricity with the exception of a relatively small number ofhydroelectric generating plants. Even in the case of hydroelectricplants such, for example, as that installed at the Grand Coulee Dam, ithas been the general practice to directly couple large water turbines tofixed electrical generators, frequently making it necessary to duplicateor provide additional equipment in order to accomodate fluctuatingdemands. Under this type of development, only the very large water powersites are developed, and smaller sites are not considered economicallyfeasible. Further, other collectively enormous sources ofnon-contaminating energy which have never been fully exploited dueprimarily to their intermittent nature: include solar energy, windenergy, and ocean tide and wave energy.

SUMMARY OF THE INVENTION

The integrated energy system according to the present invention may beconstructed in any needed size, progressively and interconnectively fromthe size needed, for example, for a small town or a single user to thatrequired to serve a continent. Each said system includes multiplediverse energy collector-converter-driven system pressure compensatedvariable volume air-compression facilities, a grid-type compressed aircombination collection-storage-transmission-distribution network,preferably made of the largest commercially available conduit-pipe whichmay be transported over the existing highway systems; and dual precisioncontrolled air-motor drives primarily for turning conventional electricgenerators. The grid conduit network preferably surrounds each area andregion of use with interconnecting grid plumbing lines into which thecompressed air is introduced and from which it is withdrawn where and asneeded. The grid plumbing system incorporates means for automatically ormanually isolating individual modules of the entire system to therebyisolate trouble spots, or areas under construction, etc.

A grid module surrounding each predetermined area or region of need isfed from multiple diverse energy source collector-converter driven aircompressor stations. Such stations are placed at points throughout thearea of need where constant energy output sources are available for useas well as at all other points of need where intermittent energy sourcesare available.

While it is contemplated that various conventional or knowncollector-converters of diverse forms of energy will be used to furnishmechanical torque for driving the air compressor stations, an improvedwind powered energy collector-converter according to the presentinvention is particularly well suited for driving the air compressorunits, for high capacity production of compressed air.

The grid type compressed air system allows the use of the compressed airfor driving conventional electrical generators which may be locatedwherever needed and convenient to population centers.

The compressor stations employed to compress the air are preferably of athree stage capability, with the inlet of the second and third stagesbeing connected so that the various compressor stations can produce highvolumes of air at relatively low pressures: and by system pressurecompensating automatic connecting of the inlets of the second and thirdstages to the discharge of the preceding stage, a lower volume ofrelatively high pressure air can be delivered as system air-pressurerises. This facilitates high-efficiency start-up of the system andassures flexibility in meeting maximum use-demands for the compressedair with minimum air compressor equipment design requirements.

While it is contemplated that, under most conditions, adequatecompressed air volume storage capacity can be provided in the multiplegrid plumbing system constructed from large diameter pipe surroundingthe major areas of use, it is recognized that in certain installationssuch as in congested sea shore cities or on islands, space requirementson shore may limit installation of such conduit systems. Under theseconditions, an offshore floating dock installation according to thepresent invention and including multiple interconnecting layers ofpiping may be joined together to provide storage for the compressed air.These floating docks are to be provided with a suitable anchorage systemto permit self-adjustment, with the docks themselves providing supportfor the multiple diverse energy collector-converter-drivenair-compressor stations.

BRIEF DESCRIPTION OF THE DRAWINGS

The foregoing and other features and advantages of the integrated energysystem according to the present invention will become more apparent fromthe detailed description thereof contained herein below, taken inconjunction with the drawings, in which:

FIG. 1 is a schematic plan view of an integrated energy system modulefor a small consumer of electricity;

FIG. 2 is a view similar to FIG. 1 and showing an integrated energysystem module for a large city or metropolitan area;

FIG. 3 is a schematic plan view of an energy recovery farm employed inthe system;

FIG. 4 is a schematic plan view of an energy recovery farm adapted foroff-shore floating use;

FIG. 5 is a schematic side elevation view of the floating energy farmshown in FIG. 4;

FIG. 6 is a sectional view of the floating energy farm of FIG. 5 on anenlarged scale with the section taken on line 6--6 of FIG. 7 and FIG. 4;

FIG. 7 is a schematic sectional view taken on line 7--7 of FIG. 6 andFIG. 4;

FIG. 8 is a schematic plan diagram of a typical compressor facilityemployed to provide compressed air for the main grid plumbing linesystem;

FIG. 9 is a schematic plan diagram of a precision RPM control system forair motor drives, for conventional electrical generators, employed inthe compressed air driven power plants;

FIG. 10 is a schematic plan diagram of a typical wind powered, verticalturbine driven air compression facility employed in the system;

FIG. 11 is a plan view of a vertical air turbine showing the bladearrangement and support framing thereof;

FIG. 12 is a sectional view of the wind turbine and air compressionfacility driven thereby;

FIG. 13 is a side elevation view of the frame structure around theperiphery of the horizontal revolving vertical wind turbine;

FIG. 14 is a fragmentary sectional view, on an enlarged scale, of thecentral hub and bearing at the base of the revolving turbine;

FIG. 15 is a fragmentary plan sectional view taken on line 15--15 ofFIG. 14;

FIG. 16 is a fragmentary sectional view of the central hub and bearingat the top of the revolving turbine;

FIG. 17 is a fragmentary sectional view taken on line 17--17 of FIG. 12;

FIG. 18 is a fragmentary plan sectional view taken on line 18--18 ofFIG. 17;

FIG. 19 is a fragmentary plan sectional view taken on line 19--19 ofFIG. 17 and showing the linkages for operating the bottom brake shoesfor the turbine;

FIG. 20 is a fragmentary sectional view taken on line 20--20 of FIG. 17.

FIG. 21 is a schematic view of a two-way air flow metering apparatusemployed in the system;

FIG. 22 is a schematic view showing an automatically and manuallytriggered isolation valve employed in the plumbing system;

FIG. 23 is a sectional view through a manhole and including a typicalmain grid line condensation blow-off means;

FIG. 24 is a fragmentary plan sectional view showing anexpansion-contraction pipe joint for use in the pipe in the conduitsystem; and

FIG. 25 is a schematic layout plan of a portion of a multiple gridsystem and illustrating the main isolation cut-off valves and typicalmodules encompassed within the grids.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

Referring now to the drawings in detail, a preferred embodiment of theinvention will be described in which numerous energy sources areutilized to compress air which is stored under pressure in aninterconnected network of transmission pipes of maximum commercial sizerequired and available which is haulable on trucks and having sufficienttotal bulk storage capacity for maintaining a long term reserve storage,and for utilizing the compressed air for the generation of electricityat or near the points of use and at a rate determined by the requirementfor electrical energy. The compressed air is utilized, throughautomatic, coordinated pressure and volume controls, to drive air motorswhich, in turn, power conventional electrical generators to supplyelectrical energy for conventional uses. The coordinated pressure andvolume controls enable the air motor to drive the generators at aprecisely controlled speed throughout the load range capabilities of thegenerators.

The transmission and storage pipe network employed in the system isdesigned in a plurality of modules which are interconnected and whichmay be automatically or manually isolated when desired or necessary,with the individual modules containing sufficient interior volumestorage capacity to operate electrical generating equipment to supplyelectrical energy to the geographical area encompassed by the module fora substantial period of time, preferably for several days. Each moduleis supplied with compressed air by multiple systems of air compressorsdescribed more fully herein below, at least a portion of which arepreferably driven by non-poluting natural energy sources such as wind,solar, thermal, water, wave, or tide powered energy collectors. However,a portion of the compressor installations in each module preferably arecapable of employing conventional power sources such as gas or steamengines or turbines.

By providing an interconnecting transmission and storage grid pipenetwork joining the respective modules, a more complete utilization ofnatural energy sources may be employed. Thus, in areas where ocean tideand wave energy, or water power from streams is generally not available,wind power turbines according to the present invention may be utilized,along with solar-power converters, as the principal sources of naturalenergy to be employed to provide the compressed air. However, as iswell-known, air movements are not uniform and it may be anticipated thatwind turbines employed in a particular module will be able to supply anexcess of air during the terms of high wind movement and be unable tosupply sufficient quantity of air during prolonged periods of relativecalm. Likewise, solar-power converters will not run at night nor oncloudy days. By interconnecting the respective modules, it is possibleto more evenly balance the system, with compressed air flowing out of aparticular module during times of high wind, and on bright and sunnydays, for example: or drawing from other modules having an extra energysupply in times of relative calm or during prolonged cloudy conditions.Due to check valve special spring loadings, small systems will releaseexcess air pressure to adjoining systems.

Only the module and grid system according to this invention makes itpossible to construct the system in steps, gradually expanding same,town by city by region, to a complete integrated national or continentalenergy system. On such a large scale, the grid network preferablyincludes a basic grid covering and dividing the entire area intorelatively large regions, with the individual towns, cities andmetropolitan areas therein each having independently operable gridsystems interconnected with each other and to the main grid system. Byuse of automatically and/or manually controlled automatic valves, entireregions as well as individual modules may be isolated. Further, metersare employed at each junction of a module to a region, or region to anational grid to measure the flow of air into or from the over-allsystem. The meter readings are then employed to compute the net supplyand utilization of compressed air by the individual modules. Thus, amodule, whether for an individual town or for a large metropolitan area,may be charged for drawing excess air from the system, or may receive apayment or credit for supplying air utilized by other modules connectedin the system.

Referring now to FIG. 1, a typical module for a small town or a largeindividual user of electrical power is designated generally by thereference numeral 10 and includes a plurality ofcollection-transmission-storage pipes 11 extending in generally parallelrelation around the user, indicated generally as a small town. Thetransmission and storage pipes 11 are interconnected as by pipe 12 topermit the free flow of compressed air between the respective pipe. Thenumber, size, and length of the transmission and storage pipes 11 willobviously be determined by the projected requirement of electrical powerto be generated and utilized within the geographical area serviced bythe module. However, it is preferred that the transmission and storagepipes 11 be of the largest needed diameter commercially available andeconomically feasible, with the length of pipe utilized being sufficientto provide a storage capacity sufficient to supply compressed air for asubstantial length of time, and preferably for several days, to operatea compressed air motor driven generator station designated generally bythe reference numeral 13.

At spaced points around the module 10 are located a plurality ofcompressor stations for supplying compressed air to the transmission andstorage pipes 11. In FIG. 1, where a generally rectangular system oftransmission and storage pipes are utilized surrounding the areaserviced by the modules, there is schematically illustrated twocompressor stations located at each corner of the module. Preferably atleast one of each of these pairs of compressor stations will be capableof utilizing a non-polluting, natural energy source, with at least aportion of the compressor stations also being capable of being driven bysolar powered or by conventional fueled steam or heat differentialengines in a relatively small module, half of the compressor stationsmay be wind turbine driven stations, designated generally by thereference numeral 14, and the other half, designated generally by thereference numeral 15, powered by solar power or by conventional fueledsteam or heat differential engines.

Initially, a module of the type illustrated in FIG. 1 may operateentirely independently of other modules; however, as more modules areinstalled, and the regional or national grid system developed, therespective modules will be connected, through a pipe 16 and meter 17 tothe grid transmission storage line 18.

The larger module shown in FIG. 2 and utilized for a larger consumer ofelectricity such as a large city or metropolitan area is quite similarin design and construction to that of the small module shown in FIG. 1,with the principal difference being size, and accordingly, similarreference numerals are used to designate similar elements in the twofigures. Thus, FIG. 2 illustrates a module, designated generally by thereference numeral 20, in which a typical city or large metropolitan areais generally surrounded by a network of transmission and storage pipes11 joined together at spaced intervals by connecting pipes 12 which, inturn, are illustrated as supplying compressed air from the system to aplurality of generating stations 13 at various locations around themodule, with the generating stations preferably being located near thehighest concentrations of electrical consumption to thereby minimizetransmission line losses.

Compressed air is supplied to the transmission and storage pipe of themodule 20 much in the same manner as that described above with regard tothe smaller module 10. However, for the larger module 20, energyrecovery farms, designated generally by the reference numeral 21 andeach consisting of a relatively large number of energycollecting-converting devices such as the wind turbine described morefull hereinbelow, are arranged in close proximity to one another in themanner illustrated schematically in FIGS. 3 and 4, to supply compressedair for the system.

Referring specifically to FIG. 3, the energy farms indicated generallyby the reference numeral 21 may comprise a plurality of individual windturbine driven compressor stations 14, and/or other diverse energydriven stations 15, each having the compressor discharge connected to acollection pipe 22, with the respective collection pipes 22 beingconnected to a header pipe 23. Header pipe 23 is connected, through aone-way check valve 24 and a cut-off valve 25, to one of thetransmission and storage pipes 11. Additional cut-off valves, orisolation valves, 26 are mounted in the lines 11. Also, an airflow meter17 is installed between check valve 24 and cut-off valve 25 to measurethe flow of air from the energy farm 21 into the transmission andstorage pipes 11. It is believed apparent that the respective compressorstations in the farm 21 may be driven by any suitable source. Thefigures 28 degrees plus 30 minutes indicate preferred-orientation ofenergy-farm quadrants with reference to prevailing winds in areas oflocation.

As can also be seen in FIG. 3, the respective needed electricalgenerating stations 13 are connected to the transmission and storagelines 11 through a cut-off valve 91, a one-way check valve 92, and ameter 93.

Referring now to FIGS. 4-7, a floating compressed air storage facilityfor use in coastal regions is illustrated. These floating installationsare preferably constructed, in the form of floating docks or floatingbarges, indicated generally by the reference numeral 30, from multipleinterconnecting and sealed layers of sections of transmission andstorage pipe 11, with alternate layers of pipe extending at right anglesto one another, as best seen in FIGS. 6 and 7. The layers of pipe areseparated by welding plates 31 at each point of contact to strengthenthe welded juncture and provide a rigid barge-like assembly. Theindividual pipe sections in each layer are interconnected by pipesection extending at 90° thereto along each end of the respective layersof pipe sections, and the layers are interconnected by verticallyextending pipe sections 32 at spaced intervals around the assembly.Preferably the welded assembly is provided with a deck surface 33 whichmay be employed to support a plurality of energy collection-conversionstations 34 (see FIGS. 8 and 10) including air compressors run bysuitable means such as tide or wave driven energy collecting devices orwind turbines of the type described more fully hereinbelow. Also, thewelded assembly is preferably equipped with a bow plate 35 to facilitatetowing and positioning of the assembly in the open water and, to thisend, one or more conventional barge tow couplings 36 may be provided onthe assembly.

To anchor the barge assemblies 30 in position, a plurality of verticalguide sleeves 37 are rigidly welded to and extend through the bargeassembly. The guide sleeves preferably have their inner surfaces linedor coated with a self-lubricating material such as Teflon to minimizefrictional contact with vertical, fixed caisson pilings 38. The pilings38 are preferably positioned by lowering through the guide sleeves 37and set by conventional means which lower the pilings to solid rock orinto tough hardpan in accordance with known procedure. The caissonpilings preferably will be made of pipe having an external diameterslightly smaller than the internal diameter of the self-lubricatingguide sleeves.

When the floating docks or barges 30 are to be positioned in water toodeep to make the use of pilings practical, a system of anchors (notshown) may be used to retain the barges in position. This may beaccomplished by using a suitable number of large anchors of conventionaldesign, with the anchors positioned outwardly from and at spacedintervals around the respective barges. Wire cables from the respectiveanchors are secured to the barge via cable tensioning winches whichmaintain a constant tensile load in the cable and thereby automaticallycompensate for vertical movement of the barge due to tide changes. Thewenches may be powered by air motors if desired, with self-operatingpressure-resistance triggered controls.

Air compressed by the compression stations 34 supported on or carried bythe floatation barges 30 and stored in the pipe sections 11 which makeup the body of the barges 30 is led from the barges to generatingstations on shore through large diameter flexible marine hose which iscommercially available and indicated as 39 in FIG. 6. The marine hose isconnected, through a standard flange coupling 40 to air flow meter 17, aone-way check valve 41 and a cut-off valve 42 to an outlet 43 connectedto the storage pipe assembly of the barge. By the use of theheavy-weighted flexible marine hose, which is permitted to lie on thebottom as it is led ashore, vertical movement of the barge can beaccommodated. From the shore, the air is led through rigid piping togenerating stations in the module service area as required.

Referring now to FIG. 8, a typical air compressor station and controlmechanism will be described in detail. The energy collecting source,whether a wind driven turbine, solar power collector-converter, or otherpower source, is indicated generally by the reference numeral 45 and isconnected, through a suitable shaft 46 and governor 47 to a hydraulictorque converter coupling 48. The coupling 48 is of a minimum speed typecontrol which gives no output rpm until optimum speed is approached orattained. The coupling 48 drives a conventional three stage compressormodified in the manner described hereinbelow or alternatively threesingle stage compressors connected together in the manner describedbelow.

In FIG. 8, the three stage compressor is indicated schematically bythree concentric circles, with the external circle 49 representing thefirst stage, the intermediate circle 50 representing the second stage,and the center circle 51 representing the third stage of the compressor.The respective compressor stages each have their inlet connected,through one-way check valves 52 and manifold 53 to atmosphere. Themanifold 53 is connected through a three-way, two position valve 54,operable to alternately connect the inlet to separate but identical airfilters 55. The relative spool position of valve 54 is controlled by amanually operated pilot valve 56 which is operated to select the filterto be used and to permit shifting of filters in response to excesspressure drop. Filter drop is measured by a conventional vacuum gauge 57connected in the manifold 53.

The respective compressor stages also have their outlets connecteddirectly to a common discharge line 58, through one-way valves 59, andconventional proportionate reduction in piston displacement where eachof the compressor stages for higher pressure is followed regardless ofwhether a single three stage compressor or three interconnected singlestage compressors are employed. However, in either case, conventionalplumbing between compressor stages is modified by the inclusions of thetwo non-return air pressure operated check valves 59 one connected inthe outlet of the first stage compressor and the other in the outlet ofthe second stage compressor, and by the inclusion of two air pressureactuated unloading valves 60 and 61 connected one between the outlet ofthe first stage compressor and the inlet of the second stage compressor,and the other between the outlet of the second stage compressor and theinlet of the third stage compressor. In normal operating conditions,valve 60 is set to unload at approximately 100 psi and valve 61 tounload at approximately 300 psi. These valves, operating in conjunctionwith the one-way check valves 52 and 59, thus allow all three compressorstages to independently draw and deliver to line 58 maximum volume lowpressure compressed air up to the unload pressure setting of valve 60 atinitial startup and at all times when system is highly overloaded. Whenthe pressure in line 58 reaches the setting for valve 60 and prior tothe pressure reaching the setting for valve 61, the first and secondstages will act as a conventional two stage compressor while the thirdstage will continue to operate as a single stage compressor taking itsinlet from the atmosphere. Upon the pressure in the system reaching thesetting for valve 61, the valve spool position will shift to open,thereby connecting the outlet of the second stage to the inlet of thethird stage, causing the three stages to then operate in the manner of aconventional three stage compressor. This operation will thereaftercontinue during all normal system operating conditions, with all threestages being serviced by the suction inlet of the first stage compressorand with all pressure outlets served, in normal succession, by thepressure outlet of the third stage. Thus, the pressure responsivecompressor control system, responding to system pressure, automaticallycontrols the compressors to deliver low, intermediate, or high pressureair, at inversely varying flow rates, to the pipe system.

Compressed air flows from the compressor unit through pipe 58 to a twoposition, three-way selector slave valve 62 which is normally springloaded to a straight through flow position and operable either manuallyor automatically as described below to the alternate position, to directthe compressed air through one or the other of two high pressure airfilters 63 and one-way check valves 64, with the discharge from therespective check valves being connected to direct the flow through meter65. The outlet of meter 65 is connected to a two-way slave shut-offvalve 66 which is normally spring loaded to the open position and whichmay be system pressure closed by manual shifting of two position,three-way pilot valve 67 from indicated normal position "a" to closingposition "b." From main shut-off valve 66, air flows through a one-waycheck valve 68 and a manually operated shut-off valve 69 to dischargeinto the transmission and storage pipe 11.

In the valve operation just described above, main line pressure is fed,through a shut-off valve 70 and a pressure reducer 71 to thetwo-position, manually actuated pilot valve 67 to supply actuatingpressure to the shut-off valve 66. Reduced pressure is also suppliedthrough line 72 to a manually actuated pilot valve 73 for directingoperating pressure, through a suitable speed control regulating orifice74, to the filter selector valve 62. A similar metering orifice isconnected in the pressure line between valves 67 and 66.

A pipe 75 is connected in a loop around valve 62, filter 63 and checkvalves 64, and a differential pressure gauge 76 is connected in line 75to give a visual indication of the pressure loss across the filter 63actually in use, and act as an indicator directing the operator when heis to actuate the valve 73 to shift from dirty to clean filter use. Astandard system pressure gauge 77 is also preferably connected to line75, and a pair of shut-off valves 78 in line 75 may be employed toisolate the gauges 76 and 77.

System air pressure is provided in a line 80 connected to compressordischarge line 58 and a spring-loaded safety valve 81, having adischarge vented to atmosphere through a silencer 82, is connected inthe line 80 to provide safety relief for the system. A second safetyvalve 83, normally set to actuate at a pressure lower than safety valve81, is connected to line 80, through a valve 84. The outlet of safetyvalve 83 is connected, through a pressure reducing valve 85 to line 86leading to clutch 48 to automatically disengage the clutch in the eventof overpressurization of the system. Simultaneously, pressure isapplied, through speed control orifice valves 74, to a brake or dampersystem 87 for shutting down the power source 45. A speed control ofificevalve 74 is also connected in line 86 between the pressure reducingvalve 85 and the clutch 48.

A high pressure line 88 bypasses safety valve 83 and is connected to apressure reducing valve 89 for supplying reduced air pressure to pilotvalve 56 for controlling, through speed control valve 74, the positionof low-pressure filter selector valve 54; and to supply pressure to asecond manually actuated pilot valve 90 connected between lines 88 andline 86. Valve 90 may be manually actuated to apply pressure to line 86to manually control actuation of the brakes and disengagement of theclutch 48. In the normal operating condition, valve 90 is connected,through and adjustable speed control orifice valve 74, to atmospherethrough silencer 82 to thereby slowly bleed pressure from line 86 topermit the brakes 87 and clutch 84 to be released and ready forautomatic actuation upon return of safety valve 83 to the normal closedoperating position.

Referring now to FIG. 9, compressed air from the respective compressorstations described above flows through the transmission and storagelines 11 to electrical generating stations located at convenientpositions within the module being served. At the respective generatingstations, air flows through a normally open motor actuated, automatic ormanually controlled shut-off valve 91 and a one-way check valve 92 to aflow meter 93 and into a manifold header 94. A standard sight gauge 95is connected, through valve 96, to manifold 94 to provide a visualindication of manifold pressure.

A plurality of electrical generators 97 are operated at the generatingstation each from a separate air line from the manifold 94. Therespective generators, and their control systems, are substantiallyidentical, with four such generators being illustrated in FIG. 9.Accordingly, only one will be described in detail, it being understoodthat the description applies equally to the other generators except forthe manual start-up control for the first generator.

Air flows from the manifold 94 through a normally open manually operableshut-off valve 98 in an air line 99 to a two-position normally closedshut-off slave valve 100. Valve 100 is spring loaded to the closedposition and opened against spring pressure by system air pressuresupplied through valve 101 and line 102 through a flow restrictingorifice valve 103 in the valve 100. Connected in line 102 is a normallyclosed, solenoid-actuated pilot valve 104 for controlling the flow ofair to valve 100 during normal operating conditions. Also, to initiallystart up the system, a manually actuated, two-position, three-way valve105 provides, in one position, direct communication between the pilotvalve 104 and shut-off valve 100, and in the other position gives directcommunication between line 102 and the valve 100, bypassing thesolenoid-actuated pilot valve 104 for manual start up conditions. Themanual valve 105 is provided only for one of the generators at astation, and in the FIG. 9 embodiment is provided only in the generatorat the left side of the drawing.

From the slave valve 100, air flows through a filter 106 to amotor-actuated, variable pressure delivery reducing valve assembly 107.A high pressure gauge 109 and a pressure differential gauge 108 areconnected in a line 110 across filter 106.

From the pressure reducer assembly 107, air flows through a linelubricator 110 to a check valve 111. Connected in the line between thelubricator and check valve 111 is a pressure relief, or safety valve 112which vents to atmosphere through a suitable silencer 82. A second sightgauge is preferably connected in the line downstream of the lubricatorto provide a visual indication of the lowered line pressure.

From the check valve 111, air flows through a motor operated variableflow restriction orifice 113 to an air motor 114 which vents spent airto atmosphere preferably through a suitable silencer 82.

Air motor 114 drives a generator 97 through a shaft coupling 115, and agovernor type gravity controlled fully reversing electrical switch,actuated by a geared drive from the air motor drive shaft, senses themotor speed and controls actuation of the one or more electric motordrives of the pressure delivery reducing valve 107 and the variableorifice 113. An insufficient speed reflected on the governor switch 116will demand additional pressure and volume delivery to the air motor,and will supply current from suitable contacts in the governor switch116 and in the customary use demand meter 117 to drive the reversiblemotors in the direction to increase both volume and pressure. Anexcessive speed sensed by the governor switch 116 will reverse the flowof current to reduce pressure and volume to air motor 114. Preferably,the motors actuating the valve assembly 107 and the variable orifice 113operate through a low speed reduction gear mechanism to provideprecision control of air flow. Governor switch 116 is a conventionalitem available commercially.

To start up the system, the manual start up valve 105 is placed in the"b" position, thereby pressurizing the slave valve 100 which is shiftedto the open position at a slow rate due to the controlled flow of airthrough the orifice 103 to gradually bring up the speed of air motor 114and generator 97 to the predetermined optimum speed of rotation. As thecustomer use demand meter 117 is energized and calls for the generationof more electricity, solenoid valve 104 will be automatically energizedand opened by electrical current from contacts in the meter 117.Thereafter, valve 105 may be normally shifted back to the normal,straight through position "a" and further successive operation of thevarious electrical generator drives will be automatically controlled bythe use demand meter. By providing additional sets of contacts in theconventional use demand meter, as the output of the first generatorapproaches maximum, the second solenoid switch will be energized tobring the second generator up to speed and on line. This procedure willautomatically be followed up to the full capacity of all generator setsthrough the contacts in the use demand meter, and generators willsimilarly be dropped from the line as use demand drops.

Referring now to FIG. 10, an air compressor installation similar to thatdescribed hereinabove with regard to FIG. 8, but particularly welladapted for use with a wind turbine of the type described hereinbelow,will be described in detail. Since many of the components of thecompressor installation of FIG. 10 are identical, either actually orfunctionally, with that described with regard to FIG. 8, similarreference numerals will be used to designate similar parts. Thus, thecompressor station is preferably installed beneath the circular base ofthe air turbine frame structure and is illustrated as employing threeseparate, single stage compressors 49A, 50A, 51A corresponding to thefirst, second and third stages, respectively, of the three stagecompressor described above. The compressors each have their inletconnected, through check valves 52 to a manifold 53 which, in turn, isconnected through the two position filter selector slave valve 54 to oneof the two filters 55. Selection of the position of valve 54 iscontrolled by the pilot valve 56 as described above.

Each of the compressors have their outlets connected, through one-waycheck valves 59 to manifold piping 58 which, in turn, is connected tothe transmission and storage pipe 11 through the filter selector slavevalve 62, filters 63, check valves 64, meter 65, slave shut-off valve 66and final check valve 68. The respective compressors are driven bygeared shafts 120 which, in turn, are driven by a bull gear 121 rigidlymounted on the base of turbine hub shaft 122 journaled for rotationabout a central fixed shaft 123. The hub shaft 122 is driven by thehorizontal supports or spokes 124 for the vertical turbine blades 125.Also, suitable clutch means (not shown), are provided between thecompressor and the drive shaft 120.

A pilot operated unloading valve 60 is connected between the check valve59 of compressor 49A and the inlet of compressor 50A between thecompressor and its inlet check valve 52, and a similar pilot operatedunloading valve 61 is connected between the outlet of compressor 50A andthe inlet of compressor 51A. As described above, valves 60 and 61 areset such that, as the outlet or main system pressure reaches apredetermined minimum, valve 60 will be actuated to connect the outletof compressor 49A to the inlet of compressor 50A. Between thispredetermined minimum pressure and a second predetermined pressuresetting for valve 61, the outlet of compressor 50A and compressor 51Awill each be discharged into the system outlet; however, above thissecond predetermined pressure, valve 61 will be actuated to connect thedischarge of compressor 50A to the inlet of compressor 51A so that thethree independent compressors will thereafter operate as a single,conventional three-stage compressor in the manner described above.Controls for the operation of the clutch and braking system arefunctionally the same as described above with regards to the embodimentof FIG. 8.

Referring now to FIGS. 11 through 20 of the drawings, a wind turbineparticularly suited to drive the air compressors employed in thisinvention will be described in detail. In FIG. 12, the turbine base isset on a fixed foundation 126 which anchors and rigidly supports thefixed vertical shaft 123. Preferably, shaft 123 is in the form of alarge-diameter pipe having an access door 127 at its base, and a ladderassembly 128 mounted in the pipe permits maintenance personnel to ascendthe structure regardless of rotation of the turbine. A plurality ofmaintenance access openings 129 are also provided in the fixed shaft 123at the level of the main turbine bearings 138 and 139, illustrated inFIGS. 14 and 16 and described more fully hereinbelow.

Extending upwardly from foundation 126 is a fixed, annular framestructure 130 having mounted on its top surface and extending around itsouter periphery a plurality of guide rollers 131 (see FIG. 20) mountedin opposed pairs by horizontal stub shafts 132 supported by brackets 133which, in turn, are mounted on a support table 134 the top of which isfour-way spring loaded vertically about multiple retaining screws 135and horizontally about multiple retaining screw assembly 136 mounted onthe fixed frame 130. Additional guide rollers 131A are mounted inopposed pairs by vertical axle shafts 132A supported in brake assemblies133.

A revolving blade support wheel frame structure indicated generally bythe reference numeral 137 in FIGS. 11 and 13, is supported on the fixedframe 130 and the fixed shaft 123 for rotation about the vertical axisof the fixed shaft by the upper and lower bearing assemblies 138, 139,respectively and by an annular, flanged monorail track 140 adapted toengage and be guided and supported by the plurality of pairs of guiderollers 131 and 131A.

The rotating frame 137 includes the vertical rotating hub shaft 122having the horizontal spokes 124 rigidly mounted thereto, as by brackets141, at spaced points along the length of the shaft 122, and the outerends of the spokes, at each level, are connected by horizontal girts 142extending around the periphery of the rotating frame, and the respectivelevels of spokes are joined by vertical columns 143, as best seen inFIGS. 11 and 13. As previously indicated, the fixed vertical turbineblades are mounted on the outer ends of the spokes 124 for rotationtherewith about the vertical axis of the assembly, with the verticalturbine blades extending, in effect, throughout the heights of therotating frame assembly 137.

A plurality of adjustable sag rods, or braces 144 provide structuralintegrity for the rotating frame assembly. A fixed catwalk assembly 145is mounted on the upper end of the fixed shaft 123 which projects abovethe top of the rotating frame assembly, with the catwalk assembly 145being supported by a suitable conical truss frame assembly 146. Thecatwalk and truss assembly provides access for maintenance at the top ofthe assembly, and provides anchorage at the outer periphery of theassembly for a plurality of guide lines 147 which extend to suitableanchors 148 at spaced points around the periphery of the turbinestructure.

Referring now to FIGS. 17 through 20, the brake system is illustrated asincluding a plurality of pneumatically actuated opposed action brakeassemblies 87 mounted in pairs at spaced intervals around the frame 130in position to engage the top and bottom flanges 150, 151 respectively,of track 140, with the brake assemblies in the respective pairs engagingthe flanges on opposed sides of the central web 152. The brakeassemblies are identical in structure and operation and accordingly onlyone will be described in detail, it being understood that thedescription applies equally to the remaining brake assemblies.

As best seen in FIGS. 17 and 18, the bracket assembly 133 includes, inits central portion, a fixed shelf 153 having mounted, on its bottomsurface, a spring-biased, pneumatically actuated brake cylinder 154, therod of which projects upwardly through the shelf to actuate the brakes.Mounted on the top of the brake cylinder rod is a top actuating arm 155retained in position by a pair of locking nuts 156 on the upper end ofthe rod. A pair of horizontally extending bolts 157 are mounted, one ineach end of the arm 155, with the bolts projecting inwardly throughslots in the vertical web of bracket 133. Supported on the distal endsof bolts 157 is a brake shoe mounting bracket 158 for sliding movementalong the vertical face of the web of bracket 133. A brake shoe 159mounted on the top surface of bracket 158 is adapted to engage theundersurface of the top flange 150 to brake the rotating turbine supportframe assembly.

At the same time, a lower brake shoe 160, mounted on a second mountingbracket 161, is pressed downwardly into engagement with the top surfaceof the lower flange 151 by a second pair of the horizontal bolts 157projecting through a second pair of slots in the web of the bracket 133.Movement of the lower mounting shoe is effected by a pair of pivotedarms, each having its inner end pivotally connected to the piston rod ofthe brake cylinder 154 and its outer end pivotally connected to thehorizontal bolts 157, and having an intermediate point pivotallyconnected to an upstanding bracket 162 mounted on the shelf 153. Thus,actuation of the brake cylinder 154 by the application of air, atreduced pressure, through the line 86 and the flow restrictors 74 willproject the cylinder rod upward to simultaneously urge brake shoes intofrictional contact with both the upper and lower flanges of the track140, on each side thereof, and at spaced points around the periphery ofthe turbine frame assembly. As described hereinabove, upon leakage ofthe air pressure from the line 86, the brakes will automatically bereleased by the spring biased brake cylinder.

Referring now to FIG. 14, 15 and 16 of the drawings, it is seen that theupper bearing assembly 138 comprises a lower annular ball race 200supported on the top inner peripheral portion of the rotatable hub shaft122. The lower bearing race 200 is accurately positioned by an adjustingbracket assembly 201 which is vertically movable by nuts 202 whichengage a fixed flange 203. Once the race 200 is accurately positioned,it is locked in place by suitable set screws 204. The bottom race andthe adjusting bracket assembly is accessible from the interior of thefixed shaft 123 through the door opening 127.

The upper race 205 is mounted on the outer peripheral surface the fixedshaft 123 in position to roll on spherical ball bearing elements 206disposed between the upper and lower races. A second adjustable bracketassembly 207 supported from an annular flange 208 on shaft 123 providesmeans for adjusting the position of the bracket 207, and set screws 209are provided to firmly anchor the mounting bracket in position.

The lower bearing assembly 139 is preferably positioned at the base ofthe fixed shaft 122 and runs in an oil bath 210 within a sump in thefoundation 126. The lower bearing race 211 is mounted on the outerperiphery of the inner fixed shaft 123 by an adjustable support bracketassembly 212 substantially identical to the support bracket assembly 201but adapted to be mounted on the outer rather than the inner surface ofthe supporting shaft. Positioning of the lower race 211 may beaccomplished by the adjustable bracket 212, which is accessible throughthe oil sump 210.

The upper race 213 of the lower bearing 139 is mounted on the innerperiphery of the rotatable shaft 122, adjacent the bottom thereof, by asecond adjustable mounting bracket assembly 201 mounted in inverserelation to the mounting bracket 201 supporting the race 200 of bearing138. Access to the top bearing race 213, and its supporting bracket 201is through the access openings 127 which, as shown in FIG. 14, may beclosed by the movable door assembly 214.

Preferably, the bearing races of both the upper and lower turbinebearings are fabricated in arcuate sections which are mounted inposition and welded together, with the welded joint being subsequentlyground to provide a continuous smooth race for the balls 206. Thisenables assembly of the respective races, or sections thereof, asnecessary, through the access openings 127, with the welded joints,indicated generally at 216 in FIG. 5, being accomplished in the spacebetween the concentric shafts 122 and 123.

Referring now to FIG. 25, a section of a national grid system isschematically illustrated to indicate the isolation cut-off valveswithin the over-all system, and the manner in which these valves arelocated to isolate sections of the grid in which trouble may develop.Also illustrated schematically on FIG. 25 is the manner in which theindividual small or large modules such as those illustrated in greaterdetail in FIGS. 1 and 2 are tied into the larger regional, national orcontinental grid system whereby excess air from such a module may flow,via the grid system plumbing, to adjacent modules, or whereby air may bedrawn from adjacent modules in times of insufficient air pressure at aparticular module. Preferably, two-way meters are connected in the gridlines at the extremities of grid sections such as Section G 192 tomeasure the flow of air where needed.

As shown in FIG. 21, each module is connected to a pipe 18 of the gridsystem through a pipe 16 having connected therein a two-way meterassembly 17 for measuring the flow both from the module to the grid andfrom the grid into the module. The meter assembly consists of a pair ofautomated cut-off valve assemblies 163 located in the line 16 at eachend of the flow measuring system. The pipe 16 adjacent each valve 163 isconnected in a T-joint, with the open ends of the T being connected byparallel pipe sections 164, 165. Connected in the pipe section 165 is aone-way check valve 166 permitting flow from the module to the grid pipeonly, through a flow meter 167 which measures the quantity of airflowing into the grid. Check valve 166 is spring biased to require asubstantial predetermined pressure differential between the pressure inthe module and that in the grid to thereby assure, particularly forsmaller modules, an ample reserve supply of air by preventing the largergrid from drawing air from these smaller modules down below a requiredminimum operation level.

A second one-way check valve 168 is connected in the branch line 164 topermit flow only in the direction from the main grid piping into themodule in question. Preferably, check valve 168 is also spring loaded,with the spring loading being relatively small, functioning primarily toassure against reverse flow through a second meter 169 connected inbranch pipe 164 to measure the flow of air from the grid into themodule. It is believed apparent that, by integrating the readings frommeters 167 and 169, the net air flow from or to a module for any giventime period may be determined.

FIG. 22 illustrates schematically the operation of the automated gridisolating shut-off valves 170. These isolation valves are connected ineach grid line 18 between the points interconnection with grid linesrunning in the transverse direction as shown in FIG. 25. The respectivevalves 170 are located in manholes 171 and are actuated, through asuitable gear drive train 172 by a motor 173 which preferably is anair-actuated motor.

Actuation of the motor 173 is controlled by a three position, four-wayclosed-center slave valve 174. A spring biased damper assembly 175mounted in the grid pipe 18 adjacent the valve 170 has a cam surfacebearing upon one end of a spring-biased push rod assembly 176 extendingoutwardly through the side wall of the pipe 18 in position to engage anactuating rod for valve 174. The spring biasing pressure on rod 176 issuch that a predetermined minimum flow rate of air through pipe 18, ineither direction, will be required to tilt the damper and cause the camto press the push rod upward. Thus, in the event of a line break, oneither side of the particular valve 170, a sudden increase in flow ratethrough the pipe will push the rod 176 upward to move the valve 174 intoposition to drive motor 173 in a direction to close the valve 170. Atthe same time, a detent on the valve actuating rod 176 engages a switch177 which, through normal electrical circuits, (not shown) transmits asignal to a control panel in the manhole and simultaneously to aregional and a national monitoring center. This enables immediateidentification of trouble spots and enables immediate dispatch ofmaintenance personnel from each adjacent region in the grid serviced bythe line in question.

Main line pressure is supplied to a pipe 177 through a pair of cut-offvalves 177 and check valves 178 connected one each in line 18 on eachside of the valve 170. A pressure reducer 180 in line 177 reduces themain line pressure to that required to operate the motor, and directsthe reduced air pressure into a T-joint which directs the air through aconduit 181 through a flow control regulating orifice 182 to valve 174,and to a three position manual pilot valve 183. From valve 183, air maybe directed, depending upon the position of the valve, to a pneumaticoperating cylinder 184 through conduit 185 to shift the valve upward todirect air to motor 173 to drive the valve 170 to the closed position,or alternatively to direct air through line 186 to the operatingcylinder 187 to shift the valve to the position to drive motor 173 tomove the valve to the open position. In the third, or null position, ofvalve 183, air in the lines 185 and 186 are vented to atmosphere.

As shown in FIG. 23, at all low points in the transmission and storagepipe system, condensation drains are provided. These condensation drainsinclude an isolation valve 188 in a line from the bottom of the pipe,for example, the main grid pipe 18, leading to a collection chamber 189.A conventional ball float valve is mounted in the collection chamber 189and operates, when the condensation reaches a predetermined level, topermit main line pressure to blow the condensate, through a check valve190 and drain line 191, to a condensate storage tank 192.

Due to the large diameter and heavy wall thickness of the main gridpiping, conventional expansion loops may not be deemed practical.However, to accommodate inevitable expansion and contraction of thepipe, O-rings sealed sliding expansion joints are provided at spacedintervals, as required. These expansion joints, illustrated in FIG. 24,comprise mating male and female bolted welding flanges 193, 194respectively, with spring loaded bolt connections therebetween, weldedone to each end of the adjacent pipe sections 18.

The spring loading is provided by opposed springs 195 retained by bolts196 through outwardly projecting annular flanges. A plurality of O-ringseals 198 are provided within the telescoping overlap portion of therespective well flanges 193, 194. To prevent foreign material frominterferring with the telescoping action of the expansion joint, anannular gasket in the form of a soft rubber hose is positioned betweenthe overlying end of well flange 193 and the outwardly projecting boltflange portion of the element 194.

While I have disclosed and described preferred embodiments of myinvention, I wish it understood that I do not intend to be restrictedsolely thereto, but rather that I intend to include all embodimentsthereof which would be apparent to one skilled in the art and which comewithin the spirit and scope of my invention.

What is claimed is:
 1. For use in an energy collection, storage, anddistribution system in which compressed air is employed as a medium forstorage of energy and employed to drive generators for generatingelectricity, a wind turbine operable to drive air compressor means andcomprising, a base, a fixed central vertical column projecting upwardlyfrom said base, said vertical column being tubular in form and ofsufficient diameter to permit maintenance personnel to ascend anddescend the column during operation of the turbine, a turbine bladesupport frame, bearing means journaling said support frame for rotationabout the vertical axis of said column, a plurality of elongated,vertically extending turbine blades mounted on said support frame atspaced intervals therearound, said blades each having a concave and aconvex surface and being mounted on said support frame with theirvertical edges disposed in generally radial planes and with theirconcave surfaces facing in the same direction around said vertical axis,cooperating guide and track means on said base and said support frame atthe bottom portion thereof supporting the outer periphery of saidsupport frame, brake means on said base and operable to engage saidsupport frame to resist rotation thereof, and guy means supporting thetop of said central column against lateral movement under wind loading.2. The compressor as defined in claim 1 further comprising accessopenings in said central column adjacent said bearing means providingaccess to said bearing means for maintenance from the interior of saidcolumn, and ladder means mounted within said central column.
 3. Theturbine as defined in claim 2 wherein said support frame comprises atubular hub shaft telescopingly received over said column, said bearingmeans including antifriction bearings adjacent the top and the bottom ofsaid tubular hub shaft and disposed between said hub shaft and saidcolumn, said hub shaft including a portion projecting downwardly belowsaid turbine blades, and drive means on said downwardly projectingportion for driving air compressor means to supply compressed air foruse in the energy collection system.
 4. The wind turbine as defined inclaim 3 further comprising air compressor means operatively connected tosaid hub shaft, and control means operable in response to air pressureproduced by said air compressor means automatically actuating saidbrakes in response to excess air pressure.
 5. For use in an energycollecting, storage and distribution system in which compressed air isemployed as a medium for storage of energy and employed to drivegenerators for generating electricity, a wind turbine driven aircompressor station comprising, in combination, a base, a centralvertical tubular column projecting upwardly from said base, a turbineblade support frame mounted for rotation about the vertical axis of saidcentral column, a plurality of elongaged vertically extending turbineblades mounted on said support frame at spaced intervals therearound andbeing disposed in position to be driven by wind to rotate said supportframe about said central column, said support frame including anelongated tubular hub shaft journaled for rotation about the axis ofsaid column and projecting downwardly below said turbine blades, aircompressor means drivingly connected to said tubular shaft, saidcompressor means including a plurality of separate compressor stages,pressure sensing means for sensing the discharge pressure of eachseparate compressor stage and control means responsive to said pressuresensing means and operatively innerconnecting said compressor stages forautomatically delivering low, intermediate or high pressure air atinversely varying flow rates for use in the energy collecting, storingand distributing system and in response to the pressure in the system,and brake means responsive to the air pressure in the system forlimiting rotation speed of said turbine support frame.
 6. The windturbine driven air compressor station as defined in claim 5 furthercomprising cooperating guide and track means on said base and saidsupport frame at the lower end thereof supporting the outer periphery ofsaid support frame, and guy means supporting the top of said verticalcentral column.